EP0046788B1 - Mecanisme de presse hydraulique - Google Patents

Mecanisme de presse hydraulique Download PDF

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Publication number
EP0046788B1
EP0046788B1 EP81900640A EP81900640A EP0046788B1 EP 0046788 B1 EP0046788 B1 EP 0046788B1 EP 81900640 A EP81900640 A EP 81900640A EP 81900640 A EP81900640 A EP 81900640A EP 0046788 B1 EP0046788 B1 EP 0046788B1
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EP
European Patent Office
Prior art keywords
chamber
piston
primary piston
hydraulic press
press mechanism
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP81900640A
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German (de)
English (en)
French (fr)
Other versions
EP0046788A1 (fr
Inventor
Marcel Pierre Therond
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0046788A1 publication Critical patent/EP0046788A1/fr
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Publication of EP0046788B1 publication Critical patent/EP0046788B1/fr
Expired legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/007—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen using a fluid connection between the drive means and the press ram

Definitions

  • the present invention relates to a hydraulic press mechanism, making it possible to successively obtain a rapid approach stroke, then a working stroke with significant developed force, this mechanism comprising: a member on which the action of controlling the device is exerted for said strokes, and a main body movable along the same axis in a fixed guide bore, means being provided for non-permanent axial locking of the body relative to the control member, the body comprising a first chamber filled with fluid incompressible into which a primary piston penetrates, extending the control member along the axis of the mechanism, this chamber communicating on the one hand with an expandable socket immobilized axially in the body and able to be pressed against the wall of the bore, and on the other hand with a second cylindrical chamber in which a secondary piston is slidably mounted, the latter being integral with a rod comprising the out it intended for the use of the mechanism.
  • Such a mechanism can be used for operations such as riveting, marking, clamping of parts and, more generally, for all operations in which the working stroke can be relatively short compared to the magnitude of the approach movement.
  • the operating principle is as follows: the main body is first moved in the bore, being pushed by the control member, until the working tool comes into contact with the part to be subjected the desired operation. When the contact of the tool with this part causes a certain resistance to the penetration of the body, the control member is moved axially relative to the body, which is allowed by the non-permanent locking means between these parts .
  • the primary piston extending the control member then pressurizes the incompressible fluid circuit, causing the expansible bushing to swell which blocks the main body against the bore, thus immobilizing this body axially.
  • the pressurization of the incompressible fluid then causes the advancement of the only secondary piston, which causes the tool to describe its working stroke, with a force "multiplication" effect obtained by the fact that the section of the second cylindrical chamber , in which the secondary piston slides, is provided greater than the section of the primary piston.
  • a rapid approach stroke is thus obtained, followed by a working stroke with a large developed effort, by applying a moderate control effort at a single point of the device, on the control member, the working stroke being in principle triggered automatically the moment the tool comes into contact with the tool to be worked.
  • the device is designed as a pneumatic cylinder, as regards its control.
  • the control member is a rod secured to a third piston subjected to the pressure of the compressed air.
  • these known devices have a second compressed air supply opposite to the first, and internal conduits allowing this compressed air to be admitted to several places in the device.
  • the compressed air must be sent through several organs, some of which are mobile, and for example it is necessary to pierce in the main body of long channels located outside the axis of the device, and provide on these channels valves (see US-A-3,059,433 - Figures 4 and 5).
  • the device therefore remains complex and its manufacture is difficult and costly, if it is desired to obtain suitable operation and in particular good sealing of the valves which requires high machining precision.
  • the present invention overcomes these drawbacks by providing a press mechanism of the kind defined above, which is of simplified structure, therefore of easier and more economical construction, and of more reliable operation, and which can be controlled by a single and same organ and from a single point both for its successive strokes in the forward direction and for its return stroke, so as to make the device compatible with various solutions for its control, and in particular with mechanical actuation.
  • control member integral with the primary piston, is associated with means allowing its axial displacement control in both directions from a single end of the device, so as to constitute a common single control member for the approach run, the work run and the return run in the rest position.
  • the assembly can therefore be obtained by using conventional machining modes such as lathe machining.
  • control function is completely separate from the internal hydraulic system, and this makes it possible to envisage control by any means, mechanical or fluid, acting on a single member, the device being able to be designed as a "press" operating. from a wide variety of external sources of energy and movement, possibly from a simple manual control.
  • the single control member integral with the primary piston, is a rod provided with a rack engaged with a drive pinion, the latter being mounted on a shaft maneuvered by a member such as a lever, possibly by inserting a torque limiter.
  • the single control member integral with the primary piston, is an additional piston slidably mounted in a cylinder coaxial with the bore in which the main body slides, to constitute a pneumatic or hydraulic control cylinder.
  • the single control member secured to the primary piston may also be a tube mounted to slide and rotate in the bore where the main body slides, and connected by a thread to this body which means immobilize in rotation, the stroke of approach being obtained by simultaneous translation of the tube and the body, while the working stroke is obtained by screwing the tube onto the body, the tube comprising an operating part, preferably linked to this tube via a limiter of couple.
  • the thread which ensures, during the approach stroke, the axial connection between the control tube and the body and during the working stroke, the relative axial displacement of the control member and of the body, with amplification of the effort.
  • the control tube is linked to the primary piston and the operation of the hydraulic part is not changed.
  • a return spring is mounted in the cylindrical chamber containing the secondary piston, and exerts its action on this secondary piston in the direction opposite to the action of the incompressible fluid.
  • the spring does not only intervene during the "return” stroke caused from the single control member, but also during the “go” movement: the stiffness of the spring prevents the main body from retreating, at the end of the approach stroke, and it makes it possible to be certain that the sleeve is properly inflated and tightened against the bore, therefore that the body is immobilized axially, before the start of the working stroke.
  • the means for non-permanent locking of the body with respect to the single control member and to the primary piston comprise, for example, a calibrated valve capable of preventing the incompressible fluid from leaving the first chamber, in the direction of the expandable sleeve and of the second chamber, that is to say the one housing the secondary piston, and thus preventing the primary piston from entering the first chamber, so that the control rod in its movement drives the entire body and in particular the piston secondary, until the tool attached to the latter comes into contact with the workpiece.
  • valve by the resistance which it offers to the flow of the fluid, opposes the insertion of the primary piston into the body, and this results in a permanent effort which makes it possible to maintain an energetic contact between the tool and the object to be pressed during the entire inflation phase of the sleeve, regardless of the position in space of the device.
  • the action of the valve is therefore combined with that of the aforementioned spring retaining the secondary piston, so that the transition from the approach stroke to the working stroke takes place under the best conditions.
  • a double valve is provided at the bottom of the first chamber, one of these valves, allowing the fluid to flow back from the expandable sleeve and the second chamber, housing the other valve which opposes the flow towards the expandable socket and the second chamber.
  • This double valve allows the fluid to easily flow back to the chamber where it came from, when the single control member is brought back, first causing the recoil of the secondary piston and the release of the main body relative to the bore, then the simultaneous recoil of the control member and the body. Furthermore, the two valves being housed one inside the other can occupy a common position on the axis, which facilitates the production of the device for the reasons already explained above.
  • the primary piston has, at its end which plunges into the first chamber filled with fluid, a longitudinal groove such that, when this primary piston is in the retracted position, and only in this position, said groove puts the first chamber of the body into communication with a reserve of hydraulic fluid, delimited by the bore in which the body slides and by a movable wall in said bore and pushed by a spring, to produce a automatic compensation for variations in fluid volume.
  • FIGS. 1 to 4 represent a machine comprising a frame 1, on which a tube 2 of vertical axis 3 is fixed.
  • a body 9 which carries an expandable sleeve 19, which is immobilized axially on the one hand by a shoulder separating the two parts of distinct diameters from the body 9, and on the other hand by an annular stop orange 20.
  • the body 9 is hollowed out, so as to comprise an upper cylindrical chamber 10 connected, by an intermediate channel 11, to a lower cylindrical chamber 12.
  • At least one radial communication 21 connects the channel 11 to the inside the sleeve 19, which is filled with incompressible fluid, in particular oil.
  • the chamber 12 contains a secondary piston 15 secured to a tool 16 passing through a screwed bottom 17, a spring 18 being compressed between this bottom 17 and the underside of the secondary piston 15.
  • the upper chamber 10, the channel 11 and the part of the lower chamber 12 situated above the secondary piston 15 are filled with the same incompressible fluid as the expandable sleeve 19.
  • a primary piston 8 which has on its lower part a longitudinal groove 26 of a length such that, when the piston 8 is in the high position (shown in FIG. 1), this groove 26 puts the chamber 10 and a chamber 35 filled with the same incompressible fluid and located above the body 9.
  • the chamber 35 constituting the fluid reserve, is separated from the chamber 10 by a seal 14, retained by a ring 13 screwed to the top of the body 9 (the seal 14 not fulfilling its function in the high position of the piston 8).
  • the chamber 35 is further delimited by another seal 7 interposed between the body 9 and the tube 2, by the inner wall of this tube 2, and by a movable upper bottom 22, which is kept applied against the surface of the liquid by means of 'a spring 23.
  • the rod 4 is provided with a rack 5, in taken with a drive pinion 6 mounted on a maneuvered shaft, for example, using a lever not shown.
  • a double valve device which temporarily closes the inlet of the intermediate channel 11 located at the bottom of the chamber 10, and in doing so opposes the penetration of the primary piston 8 into said chamber 10.
  • one of the valves is disposed inside the other: a first valve 29, pushed down by a spring 30, serves as a housing for a second valve 31, urged upwards by another spring 32.
  • the part 25 to be worked is placed on the frame 1, in the axis 3 of the device described above.
  • the control rod 4 is raised; the double valve 29-31 obturates the inlet of the channel 11 and prevents any movement of fluid in the hydraulic circuit.
  • the secondary piston 15 occupies, inside the chamber 12, its highest position, and the tool 16 linked to the secondary piston 15 is removed from the part 25.
  • a first phase (see FIG. 2), the rod 4 is pushed downwards by the action of the pinion 6, itself maneuvered by the lever already mentioned.
  • the primary piston 8 penetrates in a short stroke in the chamber 10, until the groove 26 located at its lower part is entirely beyond the seal 14.
  • the fluid contained in the chamber 10, which is then closed at its upper part and at its lower part, prevents any greater penetration of the primary piston 8 and this is how the latter carries with it the body 9.
  • the tool 16, linked to the secondary piston 15 which remains in the upper position in the chamber 12 is lowered until it comes into contact with the part 25 after having described an approach stroke C (indicated in FIG. 1).
  • the section of the secondary piston 15 is such that the force F resulting from the pressure applied to this piston remains slightly less than the blocking force of the body 9 relative to the tube 2.
  • This force F due to the fact that the section of the secondary piston 15 is greater than that of the primary piston 8, will on the other hand be higher than the force applied to the rod 4 which is indeed the desired effect (obtaining a low working stroke with large developed force).
  • the rod 4 After having thus carried out the flattening operation, or the like, on the part 25, the rod 4 is brought up by a reverse rotation of the pinion 6.
  • the primary piston 8, rising with the rod 4, causes a release of the pressure pressure on the secondary piston 15.
  • the latter returns back into the chamber 12 under the upward return action exerted by the spring 18.
  • the drop in pressure inside the expandable sleeve 19 causes it to contract .
  • the sleeve thus makes the body 9 free to move relative to the tube 2.
  • the fluid flowing back from the sleeve 19 and from the chamber 12 of the secondary piston 15 lifts the valve 29 and thus passes around it in the direction of the next chamber 10 the path defined by the arrows 34 ( Figure 4).
  • the primary piston 8 thanks to the shoulder which it also has at its lower part, carries with it upwards the body 9 which thus returns to its starting position.
  • the valve 29 returns to its rest position by closing the inlet of the channel 11. The device is thus ready to accomplish another work cycle.
  • the temporary connection between the primary piston 8 and the body 9 is made by means of a mechanical locking, with ball for example and constituted in this case by a ball 42 housed in a bore formed radially in the lower part of the piston 8 and also receiving a spring 43 which tends to push the ball 42 towards the outside of its housing.
  • this ball 42 is partially housed in a groove 44 of an annular part 45 placed under the seal 14 and which is fixed relative to the body 9.
  • the displacement of the rod of the primary piston 8 is obtained by means of an additional piston 36, fixed to the upper part of the piston 8 and mounted to slide inside a cylinder 37 placed along the axis 3 in the upper region of the tube 2 which serves as a guide for the body 9 as well as a bearing surface for the expandable sleeve 19.
  • This cylinder 37 is closed at its upper part by a cover 38.
  • the piston 36 is driven by a pneumatic or hydraulic fluid, admitted into the upper chamber of the cylinder 37 through an orifice 39 of the cover 38, and it is brought back to the rest position by a spring 40 housed in the lower chamber of the cylinder 37, or indeed by any fluid introduced into this same chamber through an orifice 41.
  • the assembly thus produced constitutes a rapidly advancing jack and multiplication of force at the end of the stroke, an important advantage of which is that, whatever the position of the piece to be pressed 25 relative to the frame 1 (within the limit of the stroke of the body 9), the final force exerted will be the same and will depend directly on the pressure of the control fluid acting on the piston 36.
  • a tube 4 is connected to the body 9 by a thread 47, these two members being slidably mounted in a bore 2 of the frame 1.
  • the body 9 is here immobilized in rotation relative to the frame 1, for example by means of a screw 48 engaged in a groove 49 of the body 9.
  • the tube 4 can on the contrary turn autor of the axis 3, and it is maneuverable by means of a part 50 mounted at its top.
  • the tube 4 maneuvered using the part 50, is rotated and therefore screwed onto the body 9, which remains immobilized in rotation.
  • the tube 4 sinks into the bore 2 and it drives with it, downwards, the primary piston 8 secured to said tube.
  • the descent of the piston 8 in the hydraulic circuit increases the pressure in the latter and has the effect, on the one hand, of blocking the body 9 relative to the frame, by inflating the expandable bush 19, and on the other hand, to make the tool 16 move against the piece to be pressed 25.
  • the torque limiting device associated with the piece 50, makes it possible to limit the pressing force of the tool 16 on the piece 25.
  • This last embodiment allows, with a relatively low screwing torque, and exerted for example by hand, to obtain a force already amplified on the primary piston 8, by the effect of the thread 47, this force being in turn amplified by the secondary piston 15 pushing the tool 16.
  • the press mechanism described above finds applications in particular in the field of marking and riveting, and it can be controlled, depending on the energy sources available and the efforts to be made, by manual actuation means, mechanical hydraulic, pneumatic or others, acting on the rod 4.
  • Other applications can be envisaged in the clamping field, where rapid advance, followed by a significant clamping force is often sought.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
  • Actuator (AREA)
  • Automatic Assembly (AREA)
EP81900640A 1980-03-12 1981-03-11 Mecanisme de presse hydraulique Expired EP0046788B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8005955 1980-03-12
FR8005955A FR2477960A1 (fr) 1980-03-12 1980-03-12 Mecanisme de presse hydraulique a course rapide puis lente

Publications (2)

Publication Number Publication Date
EP0046788A1 EP0046788A1 (fr) 1982-03-10
EP0046788B1 true EP0046788B1 (fr) 1984-03-14

Family

ID=9239754

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81900640A Expired EP0046788B1 (fr) 1980-03-12 1981-03-11 Mecanisme de presse hydraulique

Country Status (12)

Country Link
US (1) US4499728A (enrdf_load_stackoverflow)
EP (1) EP0046788B1 (enrdf_load_stackoverflow)
JP (1) JPS57500275A (enrdf_load_stackoverflow)
AT (1) ATE6610T1 (enrdf_load_stackoverflow)
AU (1) AU547086B2 (enrdf_load_stackoverflow)
BR (1) BR8107434A (enrdf_load_stackoverflow)
CA (1) CA1163900A (enrdf_load_stackoverflow)
DE (1) DE3162570D1 (enrdf_load_stackoverflow)
DK (1) DK502081A (enrdf_load_stackoverflow)
FR (1) FR2477960A1 (enrdf_load_stackoverflow)
NO (1) NO152997C (enrdf_load_stackoverflow)
WO (1) WO1981002543A1 (enrdf_load_stackoverflow)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4841846A (en) * 1986-02-24 1989-06-27 Grambling William D Pneumatic actuators with liquid seals for oil and gas well swabs
JPH055297Y2 (enrdf_load_stackoverflow) * 1988-12-15 1993-02-12
US5218821A (en) * 1992-04-23 1993-06-15 Doben Limited Pressure intensifier cylinder utilizing air
US5526644A (en) * 1995-06-07 1996-06-18 Brieschke; Todd M. Oil intensifier cylinder
DE10157373A1 (de) * 2001-11-22 2003-05-28 Bosch Rexroth Ag Antriebsvorrichtung, insbesondere für die Schließeinheit, die Einspritzeinheit oder die Auswerfer einer Kunstoffspritzgießmaschine
US6779343B2 (en) * 2002-07-10 2004-08-24 Btm Corporation Air to oil intensifier
US7021172B1 (en) * 2003-04-01 2006-04-04 Perry David S Hydraulic throttle for vehicles
US7263831B2 (en) * 2004-01-06 2007-09-04 Btm Corporation Air-to-oil intensifying cylinder
US6996984B2 (en) * 2004-01-06 2006-02-14 Btm Corporation Air-to-oil intensifying cylinder
US7194859B1 (en) 2005-10-18 2007-03-27 Btm Corporation Intensifier
WO2007116421A1 (en) * 2006-04-12 2007-10-18 O.M.G. S.R.L. Force-multiplying hydraulic actuator
US7685925B2 (en) * 2007-08-15 2010-03-30 Btm Corporation Intensifying cylinder
CN109454194A (zh) * 2018-07-27 2019-03-12 宾科精密部件(中国)有限公司 流体压力驱动的压铆装置

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE157220C (enrdf_load_stackoverflow) *
US1659157A (en) * 1926-03-25 1928-02-14 American Encaustic Tiling Comp Manually-operated press
FR973652A (fr) * 1941-10-28 1951-02-13 Presse à action hydraulique, notamment pour la fabrication des articles de prothèse
FR1152415A (fr) * 1956-06-19 1958-02-17 Consortium De Rech S Pour L Ap Soupape de retenue
US3059433A (en) * 1961-02-14 1962-10-23 Hirsch George Pressure and force multiplying devices
US3266415A (en) * 1964-06-02 1966-08-16 Basil S Palmer Air-hydraulic ram
DE1284303B (de) * 1965-12-01 1968-11-28 Nemetz Josef Hydropneumatischer Druckzylinder
DE1627852C3 (de) * 1967-06-08 1974-09-19 Josef 6200 Wiesbaden-Bierstadt Nemetz Hydropneumatischer Spannzylinder
GB1373706A (en) * 1972-09-21 1974-11-13 Bromsregulator Svenska Ab Force-transmitting devices
DE2452221A1 (de) * 1974-11-04 1976-05-13 Josef Nemetz Arbeitszylinder
CA1052234A (en) * 1976-05-17 1979-04-10 Gerard G.F. Smeets Two step pressure intensifier system
DE2818337C2 (de) * 1978-04-26 1980-07-17 Haug, Paul, 7307 Aichwald Druckübersetzter hydropneumatischer
US4288987A (en) * 1978-11-11 1981-09-15 Eugen Rapp Pneumo-hydraulic booster with rapid-traverse feature
US4249380A (en) * 1979-07-25 1981-02-10 Barry Wright Corporation Two stage intensifier

Also Published As

Publication number Publication date
FR2477960A1 (fr) 1981-09-18
BR8107434A (pt) 1982-01-05
NO152997B (no) 1985-09-23
AU547086B2 (en) 1985-10-03
US4499728A (en) 1985-02-19
JPS57500275A (enrdf_load_stackoverflow) 1982-02-18
EP0046788A1 (fr) 1982-03-10
AU6783481A (en) 1981-09-23
NO152997C (no) 1986-01-08
WO1981002543A1 (fr) 1981-09-17
DE3162570D1 (en) 1984-04-19
ATE6610T1 (de) 1984-03-15
DK502081A (da) 1981-11-12
NO813816L (no) 1981-11-11
CA1163900A (fr) 1984-03-20

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